EP0975447B1 - Walzanlage für flachprodukte - Google Patents

Walzanlage für flachprodukte Download PDF

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Publication number
EP0975447B1
EP0975447B1 EP99903748A EP99903748A EP0975447B1 EP 0975447 B1 EP0975447 B1 EP 0975447B1 EP 99903748 A EP99903748 A EP 99903748A EP 99903748 A EP99903748 A EP 99903748A EP 0975447 B1 EP0975447 B1 EP 0975447B1
Authority
EP
European Patent Office
Prior art keywords
roll
face
rolling
support
cylinders
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP99903748A
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English (en)
French (fr)
Other versions
EP0975447A1 (de
Inventor
Alain Lecrivain
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Primetals Technologies France SAS
Original Assignee
VAI Clecim SA
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Filing date
Publication date
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Publication of EP0975447A1 publication Critical patent/EP0975447A1/de
Application granted granted Critical
Publication of EP0975447B1 publication Critical patent/EP0975447B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02—Shape or construction of rolls
    • B21B27/03—Sleeved rolls
    • B21B27/05—Sleeved rolls with deflectable sleeves
    • B21B27/055—Sleeved rolls with deflectable sleeves with sleeves radially deflectable on a stationary beam by means of hydraulic supports
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B21B31/22—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis mechanically, e.g. by thrust blocks, inserts for removal
    • B21B31/26—Adjusting eccentrically-mounted roll bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
    • B21B37/30—Control of flatness or profile during rolling of strip, sheets or plates using roll camber control
    • B21B37/36—Control of flatness or profile during rolling of strip, sheets or plates using roll camber control by radial displacement of the roll sleeve on a stationary roll beam by means of hydraulic supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • F16C13/022—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle
    • F16C13/024—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle
    • F16C13/026—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle by fluid pressure
    • F16C13/028—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle by fluid pressure with a plurality of supports along the length of the roll mantle, e.g. hydraulic jacks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/08—Interchanging rolls, roll mountings, or stand frames, e.g. using C-hooks; Replacing roll chocks on roll shafts
    • B21B31/10—Interchanging rolls, roll mountings, or stand frames, e.g. using C-hooks; Replacing roll chocks on roll shafts by horizontally displacing, i.e. horizontal roll changing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B21B31/22—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis mechanically, e.g. by thrust blocks, inserts for removal
    • B21B31/30—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis mechanically, e.g. by thrust blocks, inserts for removal by wedges or their equivalent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/12—Rolling apparatus, e.g. rolling stands, rolls

Definitions

  • the subject of the invention is a rolling installation of a flat product and is especially applicable to rolling at hot or cold of a metal strip or strip.
  • the invention also covers the method of setting work of such a rolling installation.
  • a rolling mill generally includes a cage fixed having two spaced apart columns connected by a spacer and between which are arranged several cylinders superimposed on parallel axes, respectively two working cylinders defining a gap for the passage of the product and one or several support cylinders.
  • trio cages only one cylinder is used support for a small diameter working cylinder, the other working cylinder having a diameter sufficient to resist by itself the applied forces.
  • the so-called quarto cages are symmetrical, and include two supporting working cylinders respectively, on the side opposite the air gap, each on a larger diameter support cylinder.
  • each working cylinder is associated with two lateral support assemblies, called inserts, arranged on the side on the other side of the working cylinder, in the space between this and the periphery of the associated intermediate cylinder.
  • the mill stands are designed to hold all of the cylinders (support, work, intermediates, ...) in a vertical clamping plane containing their axes and substantially perpendicular to the horizontal plane rolling of the product also called "pass line".
  • each cylinder is rotatably mounted on a shaft, the two of which ends each constitute a rotating journal in a bearing housed in a support piece called chock.
  • chocks are slidably mounted in fitted windows respectively in the two columns of the cage, along guide faces parallel to a clamping plane passing through the axes of the cylinders.
  • the level of the rolling plan is determined, normally, by that of the lower support cylinder which rests, by its ends, on fixed or thick shims adjustable.
  • Balancing cylinders resting on the chocks working cylinders adjust their relative levels to determine the thickness of the air gap and allow, in addition, place the cylinders at fixed dismantling rails.
  • balancing cylinders supported on the chocks from the upper support cylinder allow adjustment the level of it between a disassembly position for which cylinders can be spaced from each other and the rolling position determined by the clamping means building on the columns.
  • each window consists of an opening rectangular width corresponding to the chocks of support cylinders and extending over the entire height occupied by the cylinders, and the guide faces of the chocks of the working cylinders are arranged on projecting parts towards the inside of the window.
  • the product to be rolled having a initial thickness passes between the two working rolls whose spacing is less, so as to determine a reduction of the initial thickness by rolling the product.
  • the two working cylinders therefore tend to deviate from one of each other and each lean on a support cylinder, larger diameter, the level of which is maintained by clamping means, for example of the screw nut or jack type hydraulic, which are supported on one side on the column on the other, on the support chocks of the support cylinder.
  • clamping means for example of the screw nut or jack type hydraulic, which are supported on one side on the column on the other, on the support chocks of the support cylinder.
  • the rolling effort which tends to spread the cylinders and is taken up by the two columns of the cage, is extremely important in the case of metal strip rolling and may reach, for example, several thousand tonnes.
  • support cylinders were given a domed profile but, more recently, it has been proposed to apply to the working cylinders a bending effort, either in a positive direction of separation of their ends is in one direction negative reconciliation.
  • Same cylinders can be used to apply bending efforts and to adjust the relative levels of working cylinders.
  • an envelope type support cylinder rotating comprising a tubular casing rotatably mounted around a fixed central shaft and resting on it through a plurality of pads whose position radial can be adjusted individually to compensate bending the tree and correcting the distribution of constraints on the associated working cylinder.
  • the window must have a minimum width to accommodate the cylinder chocks and that the clamping screws or cylinders are supported in the center of each crosspiece in the clamping plane passing through the axes of cylinders, this results in some bending of the cross member which determines a slight tightening of the two vertical uprights of the column.
  • the working cylinders rest on each other and are changed in pairs while the support cylinders are changed one after another after dismantling the other cylinders and introduces intermediate support pieces.
  • the level of the upper support cylinder is adjusted by the clamping means mounted on the columns while the chocks of the lower support cylinder rest on wedges whose level can advantageously be adjusted between a raised position which determines the level of rolling plan and a lowered position for disassembly.
  • the level of the working cylinders can be adjusted using the bending cylinders which either rest directly on the cage, or on the chocks of the lower support cylinder.
  • the subject of the invention is a new type of rolling mill which optimally resolves all of the problems that have just been mentioned and still present other advantages.
  • the invention makes it possible to reduce the risk of deformation of the cage and, by Therefore, to lighten it.
  • the invention makes it possible to considerably simplify the construction of the cage support of the cylinders, to remove certain annex organs and to facilitate the operations of adjusting and replacing the cylinders, the realization of such an installation being significantly more economical.
  • the invention therefore generally applies to an installation for rolling a metal strip product comprising a fixed holding cage having two columns separated each forming a closed frame comprising two uprights, an upper cross member and a lower cross member, and limiting a central window, and at least two cylinders to parallel axes defining a product passage air gap following a rolling plan with application, between the cylinders, of a clamping force for rolling the product, at least one of the cylinders constituting a support cylinder for the application of the clamping force, said cylinder support being rotatably mounted around its axis and carried by two opposite end heads each mounted in a piece of support bearing, on the side opposite the air gap, on a bearing face of the corresponding cross member of each column,
  • the crosspiece of each column has one side support having, over the entire width of the window a concave rounded profile extending over an angular sector of minus 180 ° and the support piece of each end head of the support cylinder is supported on said crosspiece by through a support part limited by a face of contact with a convex rounded profile combined with that of the support face, so as to fit therein.
  • the invention applies especially to a rolling mill quarto or sexto type including, on each side of the plane of rolling, at least two cylinders, one cylinder respectively working around a tree with two trunnions opposite carried by chocks strung between two faces of guide parallel to the clamping plane passing through the axes of the working cylinders, and at least one support cylinder larger diameter than the working cylinder.
  • the window of each column of the cage includes, at its end opposite the rolling plane, a recess limited by one face rounded extending over an angular sector of at least 180 ° and a central part limited by two sides on which are formed parallel faces guiding chocks of the working cylinder.
  • the concave bearing face of the crosspiece and the contact face of the support part have a circular profile over a sector of at least 180 °.
  • the invention simplifies the process of disassembly and replacement of cylinders and, in particular, support cylinders, when these can be removed from the cage by moving parallel to their axis.
  • one of the columns of the cage, placed on the side disassembly is provided with a first recess for the housing a first cylinder support piece, which passes through completely said first column, and present, in all the directions, as well as said first support piece, of the dimensions larger than those of the support cylinder, so as to allow disassembly at least in a position of the latter relative to the cage, by axial displacement of said cylinder on the side of said first column, passing through said first larger recess.
  • the second cylinder support piece opposite the dismantling side and the corresponding recess in the second column of the cage present, in all directions, dimensions at most equal to those of the cylinder, the latter being thus removable in block, with its two parts support, passing through the first recess.
  • a support cylinder of the type comprising a rotating casing rotatably mounted around a fixed support beam and taking support on it via a plurality of support pads individually adjusted by cylinders.
  • the support pieces of the two heads ends of the central shaft are each housed in a recess in a corresponding end of the window of the corresponding column and limited by a bearing face concave, said support piece being surrounded, at least by the side opposite to the air gap, by a support part limited by a convex contact face conjugated to said bearing face of the recess.
  • the tightening cylinders and adjusting their relative levels is provided, at least in part, by the adjusting means individual of the radial position of each skate, said means being controlled simultaneously so as to regulate and maintain the support generator of said level at the desired level envelope on the corresponding working cylinder.
  • the support pieces of the two heads ends of the cylinder shaft are supported, respectively, on the fixed support parts of the two columns of the cage by means of adjustable thickness which constitute means for adjusting the level of the cylinder compared to the constant level determined by the parties fixed support for the windows of the two columns.
  • the support piece on each end of the shaft can be provided with an eccentric ring having two circular faces offset from each other, respectively an internal face threaded on a bearing face cylindrical formed on the end head of the central shaft and an outer face threaded into a cylindrical bore on the support piece, the angular position of said ring with respect to the support part which can be modified by rotation of the ring to adjust the level of the cylinder axis relative to the support piece.
  • the adjustment means include, at each end of the cylinder, a set of two eccentric rings mounted one in the other and each having two eccentric circular faces one relative to the other, respectively an inner ring threaded on the cylinder head and an outer ring threaded into a bore of the support piece, the positions relative angular of said rings one with respect to the other and relative to the support piece which can be changed.
  • the adjustment of the angular positions respective of the two rings with respect to the support piece determines, by combining the eccentricities, the displacement of the axis of the cylindrical bearing face of the shaft inside a circle centered on the axis of the bore and having a radius equal to the sum of the maximum eccentricities of the two rings.
  • the invention also covers several other advantageous features which are the subject of the subclaims.
  • Figure 1 is a schematic view, in section longitudinal, of a rolling stand according to the invention.
  • Figure 2 is a side view of the cage.
  • Figure 3 is a detail view of a part of support and the end of a support cylinder, in section by a plane passing through the axis of the cylinder.
  • Figure 4 shows, in front view, a part of support for an eccentric ring.
  • FIG. 5 represents, in front view, a part of support with two eccentric rings.
  • Figure 6 is a block diagram of the Figure 5 device.
  • the invention will be set out, by way of example, in the part of a quarto type rolling mill but can be applied to any type of rolling mill comprising at least one support cylinder of fairly large diameter.
  • such a rolling mill includes, as it has been indicated in FIG. 1, a fixed cage 1 having two spaced apart columns 11a, 11b between which are arranged four superimposed cylinders, respectively two cylinders of work 2, 2 'defining an air gap 15 for product passage M along a rolling plane P1, and two support rolls 3, 3 '.
  • the axes of the cylinders are substantially parallel and placed in a clamping plane P2 which normally constitutes a vertical median plane of the cage.
  • the two columns 11a 11b are combined between them at their upper part, by a spacer 11c, bolted to the inside faces of the columns which, at their lower part, rest on steel entablatures 17 bolted to the foundations.
  • each cylinder is rotatably mounted, its two opposite ends, on trunnions turning in bearings housed in chocks which are threaded in a window in each column of the cage and, for allow level adjustments while maintaining side of the cylinder, the chocks are slidably mounted each between two guide faces provided on both sides of the window and parallel to the clamping plane P2 passing through the axes of the working cylinders. Therefore, each window usually has a rectangular shape, the column constituting a closed frame comprising two vertical uprights, an upper cross member and a lower cross member.
  • each column is generally produced by molding in one single piece, so as to form a closed shaped ring rectangular.
  • each column 11a, 11b is substantially different.
  • each window 6 has a shape oblong having a central part bounded by two faces parallel and two ends each bounded by a face semi-cylindrical.
  • the guide faces 13 of the working chocks 21 are usually provided on protruding parts extending towards each other, the faces internal 63, 63 'of the two recesses 61, 61' extend advantageously on a circular sector greater than 180 °, as shown in Figure 2, each window showing a shape similar to a violin.
  • the support parts 4, 4 ′ of the two cylinders of support 3, 3 ' are associated with support parts having a shape combined with that of the concave faces 63, 63 'of the two recesses 61, 61 'so as to be completely inserted therein.
  • the clamping force exerted between the support rollers 3, 3 'during rolling is applied over the entire width of the cross member 16 of the window 11 and on a concave surface, preferably circular, which extends over a circular sector of at least 180 °.
  • the embedding effect of the cross member 16 on the two uprights 12, 12 ' is therefore not concentrated, as before, in the corners of the window and the pressure applied by the support piece 4 on the cross-member 16 is distributed in all directions around the axis 30 of the cylinder.
  • the invention can be implemented in a rolling mill comprising, as usual, clamping means such that screw or jack taking support, on one side on the cage and the other side on the chocks of the support cylinders.
  • each chock can be associated with a support piece intermediate, limited by a convex face conjugated to the face concave 63 of the recess 61 so as to be housed in the latter, the clamping means being interposed between this support piece and chock of the cylinder.
  • clamping screws are removed and do not can no longer be used to make adjustments in height of the support cylinders.
  • this height adjustment can be carried out in moving the cylinder itself.
  • at least one of the support cylinders preferably the upper support cylinder 3 is constituted of a known type of rotating envelope cylinder comprising a central shaft 34 in the form of an elongated beam on which is threaded a tubular casing 31 having an internal face 32 and an outer face 33 cylindrical and centered on the same axis 30.
  • the tubular casing 31 is kept centered on its axis 30 by two bearings 7a, 7b mounted respectively, each on an intermediate ring 72, threaded on a head end 35a, 35b of the shaft 34.
  • a plurality of adjacent pads 36 are arranged along the clamping plane P, between a bearing face 34 'of the shaft 34 turned towards the side of the working cylinder 2 and the internal face 32 of the tubular casing 31.
  • each shoe 36 is provided an outer face in the shape of a circular sector of diameter substantially equal, apart from play, to that of the internal face 32 of the casing 31 and forming a bearing pad of the casing 31, a lubricant being introduced between the face outer of each shoe 36 and the inner face of the envelope.
  • each shoe is radially movable in a direction perpendicular to the axis 30 of the envelope 31 and is associated with means for adjusting its position radial, generally consisting of hydraulic cylinders 38 bearing on one side on the pad 36 and on the other on the support face 34 'of the shaft 34.
  • each bearing 7 comprises, conventionally, a external cage 71 fixed in a bore formed at the end of the tubular casing 31 and an internal cage mounted on the intermediate ring 72, rolling elements 74, by example of tapered bearings, being interposed between the two cages.
  • the entire bearing is held by a stop 73 bearing axially on the end 35 of the shaft 34.
  • Each end head 35a, 35b of the shaft 34 is normally limited by a cylindrical face 37 centered on an axis 30 'and, to allow the radial displacement of the envelope 31 relative to the shaft 34 under the action of pads 36, a clearance (a) is left between the internal face 72 'of the intermediate ring 72 and the lateral face 37 of the head end 35 of the central shaft 34.
  • the intermediate ring 72 is provided, laterally, from two flats 76, shown schematically in Figure 2, which slide along flat faces corresponding formed on the two heads 35 of the shaft 34 and parallel to the clamping plane P in which the cylinder axes.
  • the relative position of the support ring 72 each bearing 7 relative to the shaft 34 is adjusted by a balancing cylinder 75 housed in a recess in the corresponding part of the head 35a, 35b of the shaft 34.
  • the two jacks 75 respectively carrying the two bearings 7a, 7b therefore make it possible to determine the general level of the envelope tubular 31 relative to the shaft 34.
  • the rotating envelope cylinder 3 used for the invention can benefit from all improvements previously made to the cylinders of this type.
  • the skids of setting 36 cover a fairly large angular sector, for example of the order of a quadrant or more and be associated with oil circulation means ensuring a lift effect hydrodynamic.
  • the tree central support cylinder 3 with rotating casing takes support at a constant level on the two columns 11a, 11b of the cage 1, via the support blocks 4a, 4b mounted respectively at the two ends 35a, 35b of the shaft 34.
  • end blocks can be formed, as the show Figures 1 and 2, of machined parts 4a, 4b which are simply inserted into the corresponding housings 61a, 61b formed in columns 11a, 11b and having a hollow shape conjugated.
  • the rotating envelope cylinder 3 is associated with a hydraulic system 9 comprising means individual adjustment, in position and pressure, of the cylinders associated with each of the pads 36 for supporting the envelope, and allowing each skate to be adjusted so as to control the stress distribution, for example, as a function of flatness measurements made on the rolled product, downstream of the rolling mill.
  • the cylinder 3 with a rotating envelope still allows to correct the stress distribution but essentially performs a new function. Indeed, being given that the central shaft 34 is supported at a constant level on the cage, the application of the clamping force and the adjustment the level of the relative positions of the support cylinders in the cage and the thickness of the air gap 15 between the cylinders working 2, 2 'are provided by all of the support pads 36 which determine the displacement, parallel to itself, of the tubular casing 31 and, consequently, of the generating support G in relation to a reference level constant determined by the housings 61, 61 '.
  • This controlled displacement, parallel to itself, of the tubular casing 31 can, in fact, be provided by the individual means 38 for adjusting the radial position of each of the pads 36 which are controlled simultaneously.
  • the set of pads 36 thus constitutes, on the one hand, the main means of positioning the support cylinder 3 for adjusting the levels of the cylinders and, optionally, the level of the air gap 15 and, on the other hand, the means of application of the clamping force between the working rolls 2, 2 '.
  • the lower support cylinder 3 ' is carried by two pins 35'a, 35'b rotatably mounted in chocks 4'a, 4'b, of fixed level, which are housed, like the blocks of support of the upper support cylinder 3, in housings correspondents 61'a, 61'b formed at the bottom of the two columns 11a, 11b.
  • the two support cylinders are supported on a constant level on the two columns of the cage and we can so remove the clamping screws, as well as the chocks sliding doors usually provided to allow adjustments in height of the support cylinders.
  • the working chocks 21a, 21b are, as usual, mounted sliding along guide faces 13 parallel to the clamping plane P 2 , which are advantageously provided on two hydraulic blocks 14, 14 'fixed on the two uprights 12 , 12 'of the column 11 framing the window 6 and in which are housed jacks, not shown, for adjusting the level and bending of the working cylinders 2, 2' which bear on ears 22 formed on the two sides of each chock 21 ( Figure 2).
  • Each column 11a, 11b is therefore provided with an opening roughly shaped like a violin comprising two rounded ends and a tightened central part.
  • Each support block 4, 4 ' is thus surrounded by the bearing face 63 of the recess 61, practically over its entire periphery and at least over a 180 ° sector, i.e. up to two diametrically opposite zones on which the pressures are exerted horizontally.
  • a rolling stand according to the invention will therefore be much less expensive than those of conventional design since no additional cylinder adjustment device in height is not necessary and that the weight of the columns is markedly decreased.
  • each column in the cage is consisting of a rectangular frame which is molded into one part and must then be machined very precisely to allow the application of the guide faces of the chocks which, usually consist of patches.
  • the support blocks ends of the support cylinders are completely inserted in the recesses and the pressure is distributed over their entire periphery.
  • the invention also makes it possible to simplify considerably the devices required for disassembly and replacing the cylinders.
  • the support cylinder lower is usually removed from the cage by rolling on fixed rails and the upper support cylinder is removed only after removing the working rolls, and using fairly complex devices including the implementation work is quite long.
  • the upper support cylinder 3 is supported on the cage 1 to a constant and perfectly determined level, the dismantling of this cylinder can be carried out by means of devices installed at remains.
  • Figure 2 for example, which shows a quarto arrangement using two support cylinders 3, 3 'to rotating envelope, the latter are in position disassembly, before tightening on working cylinders 2, 2 '.
  • the rails are installed in the rolling stand 1 and are extended, outside, by support of cylinders not shown and which can be different depending on the installation. Likewise we can imagine jacks or other means of producing motion necessary to remove the support cylinders 3, 3 'from the rolling stand. Removable rail sections can ensuring the connections inside the cage.
  • the support block 4b placed on the opposite side in the direction of movement, as well as the internal face 63b of the recess in column 11b has a diameter at most equal to that of the outer face 33 of the tubular casing 31 so as to pass inside the recess 61a of the opposite column without risk of surface deterioration 63a of the recess 61a and 41b of the support block 4b.
  • each support block 4 must be limited down, for example, at one side plane 46 parallel to the running plane of the strip M, so as not to interfere with the hydraulic blocks 14a, 14b between which are the chocks of the working cylinder 2.
  • the recesses 61 and the support blocks 4 can be limited by circular cylindrical surfaces like shown in Figure 2. However, it follows that for the replacement, the tubular casing 31 must first be placed in a determined position for which its axis 30 coincides with the axis 30 ′ of the external face 41 of the block of support 4 and the surface 63 of the recess 61.
  • the recesses 61 and the support blocks 4 can advantageously have a shape oblong, limited, upwards and downwards, by semi-cylindrical surfaces whose axes are spaced one distance corresponding at least to the offset of the axis of the casing 31 between the clamping position, in contact with the working cylinder, and the replacement position for which the cylinders are spread apart.
  • This provision which will be described in detail below, with reference to FIG. 4, allows extraction and replacement of the cylinder 3 without having to refocus the tubular casing 31 in a precise position.
  • the two support cylinders respectively upper 3 and lower 3 'are of the envelope type rotating, as shown in Figure 2.
  • the chocks lower 4'a, 4'b can also be accommodated, like the blocks upper support 4a, 4b, in recesses 61'a, 61'b of the two columns 11a, 11b, according to the arrangement shown in Figures 1 and 2.
  • the lower support cylinder can be mounted on shims or eccentrics allowing the displacements of the cylinder between a low withdrawal position and a position high corresponding to the pass line level.
  • the thickness of the air gap 15 is determined by adjusting the level of the upper working cylinder 2 which must be set in contact with the upper support cylinder 3. The level of this the latter therefore depends on the diameter of the working cylinder 2.
  • Level settings of the upper support cylinder 3 are carried out, according to the invention, by displacement of the rotating casing 31 by means of the set of pads 36 and jacks 75 acting in opposite directions.
  • FIG 1 there is shown schematically, and at as a simple example, a hydraulic control system 9 of the radial position of the support pads 36 of the envelope tubular 31.
  • each shoe 36a, 36b ... is controlled by at least one hydraulic cylinder 38a, 38b ... which is supplied individually, from a hydraulic power plant 91, by a circuit 92a, 92b ... on which is placed a servo-valve 93a, 93b ....
  • Each cylinder 38a, 38b can be controlled in position or in pressure, by the associated servo-valve 93a, 93b ... in function of the orders given on an individual line 94a, 94b ... by a calculation unit 94 with several inputs information 95.
  • a reference value constituting a reference of overall position of the envelope 31 is displayed over one second input 95b of the calculation unit 94.
  • This setpoint can be displayed manually or prepared by an automatic management S sequences which, taking into account the various parameters such that the characteristics of the cage and the diameters of cylinders, makes it possible to determine the levels of the envelope 31, respectively in the disassembly position and in the rolling position.
  • the calculation unit 94 also includes an input 95d of measurement signals emitted by a device 97 'for measuring flatness, for example a roller fitted with sensors. From this information, the calculation unit 94 transmits to the servovalves 93a, 93b ..., individual correction orders for pressures applied to each of the pads 36, so as to modify the distribution of constraints to correct faults measured.
  • the lower working cylinder 2 ' is maintained by its bending cylinders to a higher level and therefore lies away from the support cylinder 3 '.
  • the metal strip not being not engaged the upper working cylinder 2 rests on the 2 'lower working cylinder.
  • a pair of cylinders is then introduced into the cage of new work, by moving in the opposite direction on rails.
  • the rotating casing 31 To replace the working cylinders, the rotating casing 31 must therefore first be removed from the working cylinder 2 of sufficient height to release the two cylinders 2, 2 '.
  • this level may change depending on the diameter of the working cylinders and this is why the parts lower 41 'of the external face of the support block 4 and the internal face 63 of the recess 61, are also eccentric down. It is therefore possible to withdraw the support cylinder 3 in all envelope positions 31.
  • the chocks 4 'of the lower support cylinder 3' and the corresponding recesses 61 ′ of the columns 11 are made in the same way, at least on the disassembly side.
  • a wedge system could be used of varying thicknesses, but the invention also provides a particularly interesting adjustment system, shown on Figures 4 and 5.
  • Each support piece 4a, 4b of the central shaft 34 comprises an intermediate support part 42, consisting of a socket-shaped outer body having a circular face internal 43, in which an eccentric system is threaded, interposed between the body 42 and the end head 35 of the central shaft 34 which is limited by a lateral face cylindrical 37.
  • the eccentric system comprises at least one ring 44 having an internal face 45 threaded on the cylindrical side face 37 which is centered on an axis 30 'and an external face 43 centered on an axis 40 and threaded into a corresponding internal face of the body 42 of the support piece 4.
  • the axis 30 'from the end 35 of the central shaft can take two diametrically opposite positions, offset by distance (d), respectively, above and below the center 40 of the face internal circular 43 of the body 42 of the support part 4.
  • the adjustment range is thus increased by the distance 2d of the level of the tubular casing 31 and, consequently, the possibility of varying the diameter of the cylinders.
  • the lower support cylinder 3 ' is carried by two journals 35'a, 35'b rotatably mounted in hollow support pieces forming chocks, with interposition eccentric rings which allow, by rotation of 180 °, adjust the axis of the lower cylinder 3 'on two separated levels and thus increase the adjustment possibilities.
  • each end 35 of the shaft 34 is mounted in a set 5 of two eccentric rings mounted one in the other, respectively an inner ring 51 and a outer ring 52.
  • the outer ring 52 has two circular faces offset, respectively an internal face 53 and a face external threaded into the internal face 43 of the body 42 of the part support 4, centered on the axis 40.
  • the inner ring 51 itself has two faces eccentric circulars, respectively an external threaded face in the inner face 53 of the outer ring 52 and a face internal 54 threaded on a conjugate circular face 37 ' preferably made on a sleeve 39 threaded on the face lateral 37 of the support head 35 of the shaft 34 and, therefore, centered on the axis 30 'thereof.
  • Adjusting the angular positions of the rings eccentrics 51 and 52 can be done in the cylinder shop, in using a rotation blocking device provided, by example, of an index linked to the inner ring 51 immobilized by a removable part on the shaft 3 and, respectively, an index on the outer ring 52 immobilized on the support block 4.
  • the adjustment of the two rings eccentrics can be motorized.
  • the inner ring 51 which turns on a socket protection 39 threaded on the end 35 of the shaft 34, is provided, at its internal face 54, with a toothed crown 55 on which meshes a pinion 55 'rotatably mounted on the shaft 34.
  • the outer ring 52 threaded on the face internal 43 of external body 42 is provided on its face outer, of a toothed crown 56 on which meshes a pinion 56 'rotatably mounted on the support block 4.
  • toothed crowns 55, 56 have only been indicated only by a sector in figure 5.
  • the pinions 55 ', 56' are rotated, independently of one another by means not shown, and associated with position locating means mounted respectively, on the shaft 34 and the support block 4.
  • This horizontal offset can, moreover, be adjusted differently on the two ends 35a, 35b of the shaft 34.
  • Offset an adjustment, called "Offset" relative positions of the cylinders in the horizontal plane, so as to avoid deformation of the contact generator G, which tends to wind on the support cylinder, causing variations not controlled flattening of the cylinders, which causes rolling cage instabilities and a degradation of the flatness of the rolled product.
  • This phenomenon known as cylinder crossing, may be so corrected but it is also possible to cause a voluntary crossing of cylinders in order to control the flatness of the product.
  • the invention can include all improvements and conventional appendices, which therefore not been described.
  • a clamp device articulated, arranged between columns 11 and blocks of support 4 makes it possible to prohibit, in operation, the unwanted axial movements that can occur under the effect of the axial thrusts induced by the efforts of rolling.
  • the upper working cylinder is associated with fixed rails and placed at the level desired by the bending cylinders.
  • Removable sections of rails ensure, in known manner, the connections at the level of the cage.
  • the invention has been described in the case of a quarto rolling mill but can be applied to another type of rolling mill using at least one fairly supporting cylinder large diameter compared to working cylinders for example a sexto or Z-High rolling mill.
  • the invention can be applied to rolling mills in which the working cylinders are not carried by chocks but, for example, by balancing forks.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Fluid Mechanics (AREA)
  • Metal Rolling (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Paper (AREA)
  • Chemical And Physical Treatments For Wood And The Like (AREA)
  • Bakery Products And Manufacturing Methods Therefor (AREA)
  • Joining Of Corner Units Of Frames Or Wings (AREA)
  • Formation And Processing Of Food Products (AREA)
  • Manufacturing And Processing Devices For Dough (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)

Claims (17)

  1. Walzanlage für ein Produkt aus Metallband mit
    einem stafionären Gestell (1) mit zwei voneinander beabstandeten Ständern (11a, 11b), die jeweils einen geschlossenen Rahmen bilden, der zwei Stützen (12, 12'), einen oberen Querbalken (16) und einen unteren Querbalken (16') aufweist, und die ein zentrales Fenster (6) umgrenzen,
    mindestens zwei Walzen mit parallelen Achsen, die einen Spalt (15) für den Durchgang eines Produkts (M) entlang einer Walzebene (P1) bilden, wobei zwischen den Walzen eine Spannkraft zum Walzen des Produkts (M) angewandt wird,
    wobei mindestens eine der Walzen eine Stützwalze (3) zum Anlegen der Spannkraft bildet, wobei die Stützwalze (3) um ihre Achse drehend und an zwei entgegengesetzt gerichteten Enden (35a, 35b) gehalten ist, die jeweils in einem Tragteil (4) befesfigt sind, das auf der dem Spalt (15) gegenüberliegenden Seite auf einer Auflagefläche (63) des entsprechenden Querbalkens (16, 16') jedes Ständers (11a, 11b) aufliegt,
    dadurch gekennzeichnet, dass der Querbalken (16) jedes Ständers (11a, 11b) auf mindestens einer Seite der Walzebene (P1) mit einer Auflagefläche (63) versehen ist, die über die ganze Breite des Fensters (6) ein abgerundetes, konkaves Profil aufweist, das sich über einen Winkelsektor von mindestens 180° erstreckt, und dass das Tragteil (4) jedes Endes (35a, 35b) der entsprechenden Stützwalze (3) auf dem Querbalken (16) über ein Auflageteil (42) aufliegt, das von einer Kontaktfläche (41) umgrenzt wird, die ein abgerundetes, zu dem der Auflagefläche (63) komplementäres konvexes Profil aufweist.
  2. Walzanlage nach Anspruch 1, die auf jeder Seite der Walzebene (P1) mindestens zwei Walzen aufweist, nämlich eine Arbeitswalze (2), die sich um eine Welle mit zwei entgegengesetzt gerichteten Zapfen dreht, die von Einbaustücken getragen werden, die zwischen zwei zur Spannebene (P2) parallel liegenden und über die Achsen der Arbeitswalzen (2, 2') führenden Führungsflächen (13) eingezogen sind, und mindestens eine Stützwalze (3) mit einem Durchmesser, der größer ist als derjenige der Arbeitswalze (2), dadurch gekennzeichnet, dass das Fenster jedes Ständers (11a, 11b) des Gestells (1) zumindest auf einer Seite der Walzebene (P1) an seinem von der Walzebene (P1) abgewandten Ende eine Aussparung (61), die von einer abgerundeten, sich über einen Winkelsektor von mindestens 180° erstreckenden Fläche (63) umgrenzt wird, und einen zentralen Teil (60), der von zwei parallelen Stützseiten der Führungsflächen (13) der Einbaustücke der Arbeitswalzen (2) begrenzt wird, aufweist.
  3. Walzanlage nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, dass zumindest auf einer Seite der Walzebene (P1) die konkave Auflagefläche (63) des Querbalkens (16) und die Kontaktfläche (41) des Tragteils (4) über einen Sektor von mindestens 180° ein kreisförmiges Profil aufweisen.
  4. Walzanlage nach einem der vorstehenden Ansprüche, bei der mindestens eine Stützwalze (3) durch zu deren Achse (30) paralleles Verschieben aus dem Gestell (1) gezogen werden kann, dadurch gekennzeichnet, dass ein erster Ständer (11a) des Gestells (1) mit einer den ersten Ständer (11a) komplett durchquerenden ersten Aussparung (61a) zum Aufnehmen eines ersten Tragteils (4a) der Walze (3) versehen ist, und dass die erste Aussparung (61a) sowie das erste Tragteil (4a) in allen Richtungen Abmessungen aufweisen, die größer sind als die der Stützwalze (3), so dass diese mindestens in einer Position in Bezug auf das Gestell (1) durch axiales Verschieben der Walze (3) zum ersten Ständer (11a) hin demontiert werden kann, wobei sie die erste Aussparung (61a) mit größeren Abmessungen durchquert.
  5. Walzanlage nach Anspruch 4, dadurch gekennzeichnet, dass das zweite, von der Demontageseite abgewandte Tragteil (4b) der Walze (3) und die entsprechende Aussparung (61b) des zweiten Ständers (11b) des Gestells (1) in allen Richtungen Abmessungen aufweisen, die höchstens gleich denen der Walze (3), sind, wobei letztere so als ganzer Block mit ihren beiden Tragteilen (4a, 4b) über die erste Aussparung (61a) ausbaubar ist.
  6. Walzanlage nach Anspruch 5, dadurch gekennzeichnet, dass die Auflagefläche (63a) der ersten Aussparung (61a) des ersten auf der Demontageseite liegenden Ständers (11a) und die Kontaktfläche (41a) des entsprechenden Tragteils (4a) über einen zu der vom Spalt abgewandten Seite gerichteten Winkelsektor von mindestens 180° ein kreisförmiges Profil mit einem Durchmesser aufweisen, der etwas größer ist als der der Stützwalze (3), und dass die Auflagefläche (63b) der zweiten Aussparung (61b) des auf der gegenüber liegenden Seite angeordneten zweiten Ständers (11b) sowie die Kontaktfläche (41b) des entsprechenden Tragteils (4b) zumindest auf der vom Spalt (15) abgewandten Seite ein kreisförmiges Profil mit einem Durchmesser aufweisen. der höchstens gleich groß ist wie der der Walze (3).
  7. Walzanlage nach Anspruch 6, dadurch gekennzeichnet, dass bei einem zwischen zwei senkrecht von einander beabstandeten Positionen verstellbaren Niveau der Enden (35a, 35b) der Walze (3) jedes Tragteil (4a, 4b) der Walze (3) durch eine im Querschnitt längliche Kontaktfläche (41) begrenzt ist, die zwei einander gegenüberliegende halbkreisförmige Flächen umfasst, deren Zentren voneinander durch eine Entfernung beabstandet sind, die die Positionseinstellungen erlaubt, und dass jede der entsprechenden Aussparungen (61a, 61b) der beiden Ständer (11a, 11b) von einer Auflagefläche (63a, 63b) begrenzt ist, die eine hohle längliche, zu der des entsprechenden Tragteils (4a, 4b) komplementäre Form aufweist.
  8. Walzanlage nach einem der Ansprüche 4 bis 6, dadurch gekennzeichnet, dass die beiden Tragteile (4a, 4b) der Enden (35a, 35b) der Stützwalze (3) mit Rollen (81) versehen sind, die auf Schienen (8) laufen, die auf dem Gestell (1) befestigt sind und sich zwischen den beiden Ständem (11a, 11b) erstrecken und zur Demontage der Walze (3) durch Rollen auf diesen Schienen (8) dienen.
  9. Anlage nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass zumindest eine Stützwalze (3) vom Typ mit drehendem Mantel ist, und zwar mit einer zentralen Welle (34), die einen länglichen Tragbalken mit zwei entgegengesetzt gerichteten, jeweils in einem Tragteil (4a, 4b) angebrachten Enden (35a, 35b) bildet, einem röhrenförmigen, sich um die zentrale Welle (34) drehend angebrachten Mantel (31) mit einer zylindrischen Innenfläche (32) und einer zylindrischen Außenfläche (33), die auf eine Drehachse (30) zentriert sind, mehreren nebeneinander entlang der zentralen Welle (34) zwischen dieser und der Innenfläche (32) des Mantels angeordneten Auflagekufen (36) und Mitteln (38) zum Einstellen jeder einzelnen radialen Position jeder Auflagekufe (36) in Bezug auf die zentrale Welle (34), und dass die Tragteile (4a, 4b) der beiden Enden (35a, 35b) der zentralen Welle (34) jeweils in einer am entsprechenden Ende des Fensters (6) des entsprechenden Ständers (11a, 11b) angebrachten Aussparung (61) untergebracht sind und von einer konkaven Auflagefläche (63) umgrenzt sind, wobei das Tragteil (4a, 4b) zumindest auf der vom Spalt (15) abgewandten Seite von einem Auflageteil (42) umgeben ist, das von einer konvexen, zur Auflagefläche (63) der Aussparung (61) komplementären Kontaktfläche (41) umgrenzt ist.
  10. Anlage nach Anspruch 9, dadurch gekennzeichnet, dass die Gesamtheit aller Mittel (38) zum Einstellen jeder einzelnen Position der Kufen (36) ein Mittel zum Anlegen der Spannkraft zwischen den Walzen bildet, wobei die Kufen (36) gleichzeitig so gesteuert werden, dass der Mantel (31) auf der gewünschten Ebene in Bezug auf die Walzebene (P1) eingestellt und gehalten wird.
  11. Walzanlage nach Anspruch 10 mit zwei Arbeitswalzen (2, 2') und zumindest einer Stützwalze (3) vom Typ mit drehendem Mantel, dadurch gekennzeichnet, dass sie Mittel zum Einstellen eines dem gewünschten Spalt entsprechenden Abstands der Arbeitswalzen (2, 2") und Mittel zum gleichzeitigen Steuern der Einstellmittel (38a, 38b...), die jeweils mit den Kufen (36a, 36b...) zum Herstellen des Kontakts zwischen dem drehenden Mantel (31) und der dazu gehörenden Arbeitswalze (2) und zum Anlegen der Spannkraft kombiniert sind, aufweist.
  12. Walzanlage nach einem der Ansprüche 10 und 11, bei der die radiale Position jeder Kufe (36a, 36b,...) in Bezug auf die Welle (34) durch mindestens einen hydraulischen Zylinder (38a, 38b,...) eingestellt wird, der zu einem Versorgungssystem (9) gehört, das eine Hydraulikzentrale (91), getrennte, jeweils mit einem Servoventil (93a, 93b,...) versehene Kreisläufe (92a, 92b....) zur Versorgung jeder einzelnen Kufe (36a, 36b,...) und eine Einheit (90) zum Regeln der Drücke, die an jede der Kufen (36a, 36b,...) in Abhängigkeit von der von einem jeder Kufe (36a, 36b,...) zugeordneten jeweiligen Positionsmessorgan (96a, 96b,...) erfassten radialen Position angelegt werden, aufweist, dadurch gekennzeichnet, dass die Regeleinheit (90) eine Recheneinheit (94) umfasst, die mindestens eine Serie (95a) Eingänge für von den einzelnen Positionsmessorganen (96a, 96b,...) gesendete Positionsmesssignale, einen Eingang (95b) eines einer globalen Positionsreferenz des drehenden Mantels (31) entsprechenden Sollwertsignals, einen Eingang (95c) eines Signals zur Stärkenkorrektur und eine Reihe Eingänge (95d) einzelner Ebenheitsregelungssignale, die eine Korrektur des an jede der Kufen (36a, 36b,...) angelegten Drucks bestimmen, aufweist.
  13. Anlage nach einem der Ansprüche 9 bis 12, dadurch gekennzeichnet, dass sie zwei Mittel zum Einstellen des relativen Niveaus der Stützwalze (3) mit drehendem Mantel in Bezug auf die Arbeitswalze (2) umfasst, nämlich jeweils ein Einstellmittel für die globale Position des drehenden Mantels (31) in Bezug auf die zentrale Welle (34) und ein Mittel (44, 5) zum Einstellen der Position der beiden Enden (35a, 35b) der Walze (3) in Bezug auf die jeweiligen stationären Auflageteile (63a, 63b) der beiden Ständer (11a, 11b) des Gestells (1).
  14. Walzanlage nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass jedes Auflageteil (4) eines Endes (35a, 35b) der Walze (3) mit Mitteln (44, 5) zum Justieren des Niveaus des Endes (35a, 35b) in Bezug auf die Auflagefläche (63) des Querbalkens (16) versehen ist.
  15. Walzanlage nach Anspruch 14, dadurch gekennzeichnet, dass die Justiermittel mindestens einen zwischen einem ringförmigen Auflageteil (42) des Tragteils (4) und dem Ende (35) der Walze (3) eingefügten Exzenterring (44) umfassen, wobei der Ring (44) zwei kreisförmige zueinander exzentrische Flächen umfasst, nämlich jeweils eine Innenfläche (45), die auf eine zylindrische am Ende (35) der Walze (3) angeordnete Auflagefläche (37, 37') aufgezogen ist, und eine Außenfläche, die in eine den ringförmigen Auflageteil (42) nach innen abgrenzende zylindrische Bohrung (43) eingezogen ist, wobei die Winkelposition des Rings (44) in Bezug auf das Tragteil (4) durch Drehen des Rings (44) geändert werden kann, um das Niveau der Achse (30') der zylindrischen Auflagefläche (37, 37') des Endes (35) des Zylinders (3) in Bezug auf das Tragteil (4) zu justieren.
  16. Walzanlage nach Anspruch 14, dadurch gekennzeichnet, dass die Justiermittel eine Einstelleinheit (5) umfassen, die zwischen einem ringförmigen Auflageteil (42) des Tragteils (4) und dem Endkopf (35) der Walze (3) eingefügt ist, wobei die Einheit (5) zwei exzentrisch ineinander montierte und jeweils zwei kreisförmige, zueinander exzentrische Flächen aufweisende Ringe umfasst, und zwar einen auf das Ende (35) aufgezogenen Innenring (51) und einen Außenring (52), der in eine das Auflageteil (42) des Tragteils (4) nach innen begrenzende Bohrung (43) eingezogen ist, wobei die relativen Winkelpositionen der Ringe zu einander und in Bezug auf das Tragteil (4) geändert werden können.
  17. Walzanlage nach Anspruch 16, dadurch gekennzeichnet, dass die Einstellung der jeweiligen Winkelpositionen der beiden Ringe (51, 52) in Bezug auf das Tragteil (4) die Verschiebung der Achse (30') der zylindrischen Auflagefläche (37) des Endes (35) durch Kombinieren der exzentrischen Lagen innerhalb eines Kreises bestimmt, der auf die Achse (40) der Bohrung (43) zentriert ist und einen Radius hat, der der Summe der maximalen exzentrischen Lagen der beiden Ringe entspricht.
EP99903748A 1998-02-13 1999-02-12 Walzanlage für flachprodukte Expired - Lifetime EP0975447B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9801784 1998-02-13
FR9801784A FR2774929B1 (fr) 1998-02-13 1998-02-13 Installation de laminage de produits plats et son procede de mise en oeuvre
PCT/FR1999/000322 WO1999041026A1 (fr) 1998-02-13 1999-02-12 Installation de laminage de produits plats

Publications (2)

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EP0975447B1 true EP0975447B1 (de) 2003-05-02

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EP (1) EP0975447B1 (de)
JP (1) JP4399034B2 (de)
KR (1) KR100558672B1 (de)
CN (1) CN1151003C (de)
AT (1) ATE238849T1 (de)
CA (1) CA2286566A1 (de)
DE (1) DE69907330T2 (de)
ES (1) ES2193683T3 (de)
FR (1) FR2774929B1 (de)
TW (1) TW424008B (de)
WO (1) WO1999041026A1 (de)

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US6643883B1 (en) * 1998-10-26 2003-11-11 Mitsubishi Heavy Industries, Ltd. Wiper for liquid substances
FR2812082B1 (fr) * 2000-07-20 2002-11-29 Vai Clecim Rouleau de mesure de planeite
DE102008015826A1 (de) 2008-03-27 2009-10-01 Sms Siemag Aktiengesellschaft Walzgerüst
CN101450374B (zh) * 2008-12-23 2012-06-27 中国重型机械研究院 一种电磁搅拌支撑辊装置
JP2013006199A (ja) * 2011-06-27 2013-01-10 Ntn Corp バックアップロール軸受装置
JP2013185673A (ja) * 2012-03-09 2013-09-19 Ntn Corp バックアップロール軸受装置
FR3078494B1 (fr) * 2018-03-05 2021-12-17 Fives Dms Procede de laminage avec etape de reajustement de l'inter-espace entre le cylindre d'appui lateral et le cylindre de soutien
CN113000604B (zh) * 2021-02-08 2022-02-11 太原科技大学 一种轨道交通用大型车轴智能楔横轧机

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US2106866A (en) * 1934-10-15 1938-02-01 Frank A Best Metalworking machine
US3355924A (en) * 1963-07-10 1967-12-05 Sendzimir Inc T Control of deflection in rolling mills and the like
CH624592A5 (de) * 1978-02-07 1981-08-14 Escher Wyss Ag
DE3109536C3 (de) * 1981-03-13 1994-04-14 Escher Wyss Ag Regelanordnung für ein Quarto-Metallwalzwerk
DE3211378A1 (de) * 1982-03-27 1983-12-29 Mannesmann AG, 4000 Düsseldorf Walzenstuetzeinrichtung fuer den arbeitswalzenwechsel an walzgeruesten
CH656812A5 (de) * 1982-04-08 1986-07-31 Escher Wyss Ag Walzvorrichtung.
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FR2599646B1 (fr) * 1986-06-04 1991-09-20 Clecim Sa Cylindre de laminoir a enveloppe tournante
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GB8920763D0 (en) * 1989-09-13 1989-10-25 Davy Mckee Poole Controllable deflection roll
JPH04237505A (ja) * 1991-01-16 1992-08-26 Kobe Steel Ltd 回動リング式圧下装置

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CN1151003C (zh) 2004-05-26
JP4399034B2 (ja) 2010-01-13
JP2001520586A (ja) 2001-10-30
ES2193683T3 (es) 2003-11-01
FR2774929A1 (fr) 1999-08-20
EP0975447A1 (de) 2000-02-02
FR2774929B1 (fr) 2000-06-09
ATE238849T1 (de) 2003-05-15
DE69907330T2 (de) 2004-03-25
US6151944A (en) 2000-11-28
CN1258237A (zh) 2000-06-28
CA2286566A1 (fr) 1999-08-19
TW424008B (en) 2001-03-01
DE69907330D1 (de) 2003-06-05
KR100558672B1 (ko) 2006-03-10
KR20010006333A (ko) 2001-01-26
WO1999041026A1 (fr) 1999-08-19

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